EP1688632B1 - Universal joint lubrication improvements - Google Patents
Universal joint lubrication improvements Download PDFInfo
- Publication number
- EP1688632B1 EP1688632B1 EP06001834A EP06001834A EP1688632B1 EP 1688632 B1 EP1688632 B1 EP 1688632B1 EP 06001834 A EP06001834 A EP 06001834A EP 06001834 A EP06001834 A EP 06001834A EP 1688632 B1 EP1688632 B1 EP 1688632B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- ball
- universal joint
- cavity
- seal
- plate
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Not-in-force
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
- F16D3/26—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected
- F16D3/36—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected in which each pivot between the coupling parts and the intermediate member comprises a single ball
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
- F16D3/26—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected
- F16D3/30—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected in which the coupling is specially adapted to constant velocity-ratio
- F16D3/32—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected in which the coupling is specially adapted to constant velocity-ratio by the provision of two intermediate members each having two relatively perpendicular trunnions or bearings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/84—Shrouds, e.g. casings, covers; Sealing means specially adapted therefor
- F16D3/843—Shrouds, e.g. casings, covers; Sealing means specially adapted therefor enclosed covers
- F16D3/848—Shrouds, e.g. casings, covers; Sealing means specially adapted therefor enclosed covers allowing relative movement of joint parts due to sliding between parts of the cover
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T403/00—Joints and connections
- Y10T403/32—Articulated members
- Y10T403/32606—Pivoted
- Y10T403/32631—Universal ball and socket
Definitions
- This invention relates to improving lubrication in a universal joint, particularly in a double cardan universal joint.
- a universal joint having a double-cross link is known from EP-A-0469396 A1 .
- a constant velocity joint having a centering disk bearing eccentric socket is known from US 5,419,740 .
- a centering apparatus for constant velocity universal joint is known from US 4,650,439 .
- the invention in one aspect provides an elastomeric seal for a ball and socket centering apparatus of a universal joint.
- an elastomeric seal is bonded to a metal or other rigid strong material ball retainer ring that has an internal spherical surface in sliding contact with the external spherical surface of a centering ball of the universal joint.
- the elastomeric seal is bonded at an outer end of the ball retainer so as to wipe against a spherical surface of the ball as the ball rotates relative to the ball retainer. The seal wipes against the ball as the ball rotates relative to the retainer to retain lubricant in the socket in which the ball is received.
- the seal in a free state extends radially inward relative to the retainer, beyond the spherical surface of the retainer so that when, if placed in mating contact with the retainer, the ball compresses the seal radially outward, so that the seal presses against the spherical surface of the ball with sufficient force to retain the lubricant in the socket.
- the retainer spherical surface is shaped such that it interferes with withdrawal of the ball from the socket.
- the seal is not subjected to the significant forces that act on the ball to withdraw it from the socket, but those are borne by the retainer which is made of a rigid material such as steel or another strong or rigid material.
- a seal of the invention helps retain lubricant in the ball socket and helps keep dirt out of the socket and away from the ball retainer.
- the seal follows the contour of the outside of the ball as the drive line that includes the universal joint is angled. This feature decreases the need to lubricate the ball socket area more often and extends the mechanical life of the ball and socket.
- the invention provides a universal joint housing that contains lubricant to lubricate a moving center plate and floating wear plates. Over a period of time, a housing of a constant velocity universal joint needs to be re-lubricated because the lubrication pumps out of the housing as the center plate moves to the outer edge of the lubricated cavity in the housing as the housing rotates.
- the invention seeks to increase the length of the lubrication period and decrease the wear generated in the sliding area of the housing by adding cavity plates on each face of the housing that also act as wear plates. Each cavity plate acts like a labyrinth mechanical seal as it captures the lubricant behind it in a reservoir groove in the housing.
- the reservoir replenishes the moving surfaces with lubrication in an extended period of time, decreasing the frequency of the need for lubrication.
- the pumping action of lubricant still takes place but the lubricant is captured in the reservoir behind the cavity plate, keeping the lubricant available longer as the lubricant in the cavity is used up.
- the material of the cavity plate also acts as an enlarged wear area (enlarged relative to if it was not present) and therefore should be chosen to be strong and wear resistant.
- Some materials that may be used for these plates include spring steel, nylon and other wear resistant plastics and metals.
- seals can be provided between the retainer and the ball socket, between the centering plate and the wear plates and between the wear plates and the cavity plates.
- One or more lubrication passageways can be provided in the centering plate that communicate with the ball sockets through an orifice so as to regulate lubricant flow between the center cavity and the ball sockets.
- Fig. 1 is a cross-sectional view of a double cardan universal joint incorporating aspects of the invention
- Fig. 2 is a cross-sectional view like Fig. 1 illustrating the universal joint of Fig. 1 at an extreme angle;
- Fig. 3 is a detail view of the right-hand ball socket area of the universal joint of Fig. 2 , the left-hand ball socket area being a mirror image of Fig. 3 ;
- Fig. 4 is a partial section view of the ball retainer seal illustrated in Figs. 1-3 ;
- Fig. 5 is a detail view of the upper portion of Fig. 4 ;
- Fig. 6 is a axial plan view of one of the cavity plates illustrated in Figs. 1 and 2 .
- Fig. 7 is a view similar to Fig. 1 of a second embodiment of the invention.
- Fig. 8 is a view similar to Fig. 3 of the embodiment of Fig. 7 ;
- Fig. 9 is a view similar to Fig. 2 of a third embodiment of the invention.
- Fig. 10 is a partial cross-sectional view of an alternative centering plate for the three embodiments illustrated.
- Fig. 11 is a view like Fig. 10 but of another alternative centering plate.
- a double Hooke's type universal joint 10 has a housing 12 and a pair of yokes 14 connected to the housing 12 by a pair of respective cross links 16 in well known manner.
- Each yoke 14 defines at its inner end a ball socket 18 ( Fig. 3 ) in which is received a ball 20 having an external spherical surface 22 and an internal cylindrical surface 24 in which is slidibly received a pin 26 of a centering plate 28 that slides in a center cavity 29 of the housing 12.
- the spherical surface 22 of the ball 20 mates with the internal spherical surface 29 of the ball cavity 18 and also mates with an internal spherical surface 30 of a ball retainer 32.
- the surface 30 captures the ball 20 in the ball socket 18 as it is made of steel or another rigid material that fixes the ball 20 in the socket 18 while permitting sliding movement of the spherical surface 22 against the spherical surfaces 30 and 28.
- the ball retainer 32 is held in the inner end of the yoke 14 by a snap ring 34 that fits in an external groove of the retainer 32 and fits in an internal groove in the end of the yoke 14.
- the hard and rigid part of the retainer 32 is referred to as the body portion 36 of the retainer 32 and the seal portion 40 is referred to as such herein.
- the seal portion 40 is bonded in a recess at the exterior end of the body portion 36 and has a generally U-shaped cross-section as illustrated in Figs. 4 and 5 .
- the seal 40 is made of an elasotmeric material such as a natural or synthetic rubber. One common material for the seal found suitable is black viton.
- the body portion 36 of the retainer 32 is a relatively hard and rigid material such as steel, as it bears most of the load that retains the ball 20 in the ball socket 18.
- the seal 40 has an outer leg portion 42, a connecting bridge portion 44 and an inner leg portion 46 extending from the inner end of the connecting portion 44.
- the outer portion 42 and the bridge 44 are bonded to the recessed surface 48 at the outer axial end of the body portion 36 of the retainer 32.
- the inner leg portion has a curved inner surface 50 that is shaped to conform to the spherical surface 22 of the ball 20 and that, in its free state, is radially inward of the surface 30 of the body portion 36.
- the ball presses the surface 50 and the inner leg portion 46 radially outwardly with a force such that the coating of lubricant on the surface 22 of the ball 20 is wiped backwardly toward the ball recess 18 by edge 52 of the seal 40 so as to keep the lubricant largely inside of the edge 52.
- the opposite or outer end of surface 50, at 54 (its outer edge) is curved so as not to scrape or wipe lubricant on the surface 22 outwardly when the ball surface 22 retreats inwardly past the end 54. Thereby, lubricant on the surface 22 is impeded from going outside of the ball recess 18 past edge 52, and the reentry of the lubricant film on the surface 22 is facilitated by the shape of the end 54.
- the inner leg 46 can resiliently deflect outward as shown at 60 in Fig. 3 when it comes into contact with the pin 26.
- the seal 40 can spring back to its normal position, shown at the opposite side of the seal in Fig. 3 .
- the seal 40 can spring back to the position shown in Fig. 5 .
- the universal joint 12 has a pair of cavity plates 62 which are annular in shape as shown in Fig. 6 .
- the cavity plates 62 are received in recesses formed in the housing 12, one on each side of the centering plate 28, so that they form surfaces against which wear plates 64 slide.
- the cavity plates 62 partially close off the open end of the lubrication reservoirs 66 that are formed in each half of the housing 12. By closing these openings of the reservoirs 66 off, the cavity plates 62 impede the escape of lubricant from the reservoirs 66.
- the cavity plates 62 enlarge the area of the wear surfaces of the cavity 29 defined by the housing 12 in which the centering plate 28 and wear plates 64 are received and orbit, they reduce wear of the wear plates 64. In addition they make it less likely that the centering disc 28 or wear plates 64 will tip relative to the housing 12 in the cavity 29 in which the centering plate 28 and wear plates 64 orbit.
- the cavity plate 62 should be made of a dimensionally stable material that presents a good wear surface, such as steel, nylon or a similar material. For example, one material found suitable is spring steel.
- the cavity plates 62 are received in grooves, one formed in each housing half (the housing halves are bolted together to form the housing 12) and are kept in these grooves by the centering plate 28 and wear plates 64 holding the cavity plates 62 spaced apart.
- the cavity plates 62 could be bonded or otherwise secured to each housing half.
- Figs. 7 and 8 illustrate a second embodiment 110 that is very similar to the first embodiment 10.
- elements corresponding to elements of the first embodiment 10 are labeled with the same reference number plus 100.
- the embodiment 110 differs from the embodiment 10 in that it has an additional seal 172 between the ball retainer 132 and the ball cavity 118, to help retain lubricant in the ball cavity, and has an additional seal 174 on each face of the centering plate 128, at each circumferential corner as illustrated in Fig. 7 .
- a seal 178 is also provided at the inner diameter of each plate 162 and is bonded thereto to create a sliding seal with the adjacent plate 164
- the seals 174 and 178 help retain lubricant in the center cavity 29 area of the housing 112.
- the seals 172 and 174 could be provided as o-ring seals as illustrated, or could be provided as bonded-on lip seals like the seal 40.
- FIG. 9 A third embodiment 210 having additional seals is illustrated in Fig. 9 .
- elements corresponding to elements of the second embodiment 110 are labeled with the same reference number plus 100.
- the embodiment 210 differs from the embodiment 110 by having an alternative for the seal 174, which is a band seal 276 provided around the outside circumference of the centering plate 28 as illustrated in Fig. 9 .
- the edges of the seal 276 create a sliding seal with the plates 264 that helps retain lubricant in the center cavity 229 of the housing 212.
- Seals 172 are not illustrated in this embodiment, but could be.
- Figs. 10 and 11 illustrate alternative lubrication passageways 79 and 80 running radially through the centering plate 28 that communicate with axial passageway 82 of embodiment 10. Only one is shown in each centering plate although more than one may be provided.
- the passageway 82 runs through the plate 28 and pins 26 to provide communication between the ball sockets 18, and the passageway 79 or 80 provides communication from the center cavity 29 of the housing to the passageway 82, and therefore to the ball sockets 18.
- Fig. 10 illustrates the passageway 79 made using a center drill and
- Fig. 11 illustrates the passageway 80 made using a standard drill bit and controlling the drill point break-through depth.
- Both passageways 79 and 80 have a smaller diameter hole at its inner end that acts as an orifice to regulate the flow of grease passing between the center cavity grease reservoir and the two ball sockets. This smaller diameter hole creates resistance to flow and therefore creates a pressure difference when filling with grease and when running.
- the passageways 79 or 80 can be applied to any of the embodiments of the invention.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Pivots And Pivotal Connections (AREA)
- Sealing Devices (AREA)
Abstract
Description
- This invention relates to improving lubrication in a universal joint, particularly in a double cardan universal joint.
- It is well known that universal joints, and in particular high angle double cardan universal joints, need lubrication over a prolonged period of high speed operation, without throwing the lubrication out due to centrifugal and other forces on the universal joint. This is discussed in
U.S. Patent Nos. 4,781,662 and5,688,065 . - A universal joint having a double-cross link is known from
EP-A-0469396 A1 . - A constant velocity joint having a centering disk bearing eccentric socket is known from
US 5,419,740 . - A centering apparatus for constant velocity universal joint is known from
US 4,650,439 . - Although universal joints are well known in the art, a problem persists in retaining lubricant in the joint for as long as possible. Typically, the joint is lubricated when new. After being placed in service, the joint may never be lubricated again. The joint is subjected to centrifugal forces in service, which tend to cause the lubricant to be thrown radially outward. The invention described herein is accordingly directed to retaining lubricant in the joint during operation.
- The invention in one aspect provides an elastomeric seal for a ball and socket centering apparatus of a universal joint. According to the invention, an elastomeric seal is bonded to a metal or other rigid strong material ball retainer ring that has an internal spherical surface in sliding contact with the external spherical surface of a centering ball of the universal joint. The elastomeric seal is bonded at an outer end of the ball retainer so as to wipe against a spherical surface of the ball as the ball rotates relative to the ball retainer. The seal wipes against the ball as the ball rotates relative to the retainer to retain lubricant in the socket in which the ball is received.
- In a preferred aspect, in a free state the seal extends radially inward relative to the retainer, beyond the spherical surface of the retainer so that when, if placed in mating contact with the retainer, the ball compresses the seal radially outward, so that the seal presses against the spherical surface of the ball with sufficient force to retain the lubricant in the socket.
- In another aspect, the retainer spherical surface is shaped such that it interferes with withdrawal of the ball from the socket. Thereby, the seal is not subjected to the significant forces that act on the ball to withdraw it from the socket, but those are borne by the retainer which is made of a rigid material such as steel or another strong or rigid material.
- A seal of the invention helps retain lubricant in the ball socket and helps keep dirt out of the socket and away from the ball retainer. The seal follows the contour of the outside of the ball as the drive line that includes the universal joint is angled. This feature decreases the need to lubricate the ball socket area more often and extends the mechanical life of the ball and socket.
- In another aspect, the invention provides a universal joint housing that contains lubricant to lubricate a moving center plate and floating wear plates. Over a period of time, a housing of a constant velocity universal joint needs to be re-lubricated because the lubrication pumps out of the housing as the center plate moves to the outer edge of the lubricated cavity in the housing as the housing rotates. The invention seeks to increase the length of the lubrication period and decrease the wear generated in the sliding area of the housing by adding cavity plates on each face of the housing that also act as wear plates. Each cavity plate acts like a labyrinth mechanical seal as it captures the lubricant behind it in a reservoir groove in the housing. The reservoir replenishes the moving surfaces with lubrication in an extended period of time, decreasing the frequency of the need for lubrication. The pumping action of lubricant still takes place but the lubricant is captured in the reservoir behind the cavity plate, keeping the lubricant available longer as the lubricant in the cavity is used up.
- In this aspect, the material of the cavity plate also acts as an enlarged wear area (enlarged relative to if it was not present) and therefore should be chosen to be strong and wear resistant. Some materials that may be used for these plates include spring steel, nylon and other wear resistant plastics and metals. By adding the cavity plates to the housing, it allows the floating wear plates to have more surface area to slide on and also keeps the center plate and sliding plates parallel so there is less binding from center plate tipping. This reduces friction when constant velocity universal joints are angled at high angles during operation.
- In addition, seals can be provided between the retainer and the ball socket, between the centering plate and the wear plates and between the wear plates and the cavity plates. One or more lubrication passageways can be provided in the centering plate that communicate with the ball sockets through an orifice so as to regulate lubricant flow between the center cavity and the ball sockets.
- The foregoing and other objects and advantages of the invention will appear in the detailed description which follows. In the description, reference is made to the accompanying drawings which illustrate a preferred embodiment of the invention.
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Fig. 1 is a cross-sectional view of a double cardan universal joint incorporating aspects of the invention; -
Fig. 2 is a cross-sectional view likeFig. 1 illustrating the universal joint ofFig. 1 at an extreme angle; -
Fig. 3 is a detail view of the right-hand ball socket area of the universal joint ofFig. 2 , the left-hand ball socket area being a mirror image ofFig. 3 ; -
Fig. 4 is a partial section view of the ball retainer seal illustrated inFigs. 1-3 ; -
Fig. 5 is a detail view of the upper portion ofFig. 4 ; and -
Fig. 6 is a axial plan view of one of the cavity plates illustrated inFigs. 1 and 2 . -
Fig. 7 is a view similar toFig. 1 of a second embodiment of the invention; -
Fig. 8 is a view similar toFig. 3 of the embodiment ofFig. 7 ; -
Fig. 9 is a view similar toFig. 2 of a third embodiment of the invention; -
Fig. 10 is a partial cross-sectional view of an alternative centering plate for the three embodiments illustrated; and -
Fig. 11 is a view likeFig. 10 but of another alternative centering plate. - Referring to
Figs. 1 and 2 , a double Hooke's type universal joint 10 has a housing 12 and a pair ofyokes 14 connected to the housing 12 by a pair ofrespective cross links 16 in well known manner. Eachyoke 14 defines at its inner end a ball socket 18 (Fig. 3 ) in which is received aball 20 having an external spherical surface 22 and an internalcylindrical surface 24 in which is slidibly received apin 26 of a centering plate 28 that slides in acenter cavity 29 of the housing 12. The spherical surface 22 of theball 20 mates with the internalspherical surface 29 of theball cavity 18 and also mates with an internalspherical surface 30 of aball retainer 32. Thesurface 30 captures theball 20 in theball socket 18 as it is made of steel or another rigid material that fixes theball 20 in thesocket 18 while permitting sliding movement of the spherical surface 22 against thespherical surfaces 30 and 28. Theball retainer 32 is held in the inner end of theyoke 14 by a snap ring 34 that fits in an external groove of theretainer 32 and fits in an internal groove in the end of theyoke 14. - The hard and rigid part of the
retainer 32 is referred to as thebody portion 36 of theretainer 32 and theseal portion 40 is referred to as such herein. Theseal portion 40 is bonded in a recess at the exterior end of thebody portion 36 and has a generally U-shaped cross-section as illustrated inFigs. 4 and 5 . Theseal 40 is made of an elasotmeric material such as a natural or synthetic rubber. One common material for the seal found suitable is black viton. - As mentioned above, the
body portion 36 of theretainer 32 is a relatively hard and rigid material such as steel, as it bears most of the load that retains theball 20 in theball socket 18. Referring toFig. 5 , theseal 40 has anouter leg portion 42, a connectingbridge portion 44 and aninner leg portion 46 extending from the inner end of the connectingportion 44. Theouter portion 42 and thebridge 44 are bonded to therecessed surface 48 at the outer axial end of thebody portion 36 of theretainer 32. The inner leg portion has a curvedinner surface 50 that is shaped to conform to the spherical surface 22 of theball 20 and that, in its free state, is radially inward of thesurface 30 of thebody portion 36. Thus, when theball 20 is received in theretainer 32, the ball presses thesurface 50 and theinner leg portion 46 radially outwardly with a force such that the coating of lubricant on the surface 22 of theball 20 is wiped backwardly toward the ball recess 18 by edge 52 of theseal 40 so as to keep the lubricant largely inside of the edge 52. The opposite or outer end ofsurface 50, at 54 (its outer edge) is curved so as not to scrape or wipe lubricant on the surface 22 outwardly when the ball surface 22 retreats inwardly past theend 54. Thereby, lubricant on the surface 22 is impeded from going outside of theball recess 18 past edge 52, and the reentry of the lubricant film on the surface 22 is facilitated by the shape of theend 54. - In addition, referring to
Fig. 3 , at an extreme angle of the universal joint, theinner leg 46 can resiliently deflect outward as shown at 60 inFig. 3 when it comes into contact with thepin 26. When the angle is relieved, theseal 40 can spring back to its normal position, shown at the opposite side of the seal inFig. 3 . Or, if no ball is present immediately adjacent to the seal, theseal 40 can spring back to the position shown inFig. 5 . - In another aspect of the invention, the universal joint 12 has a pair of
cavity plates 62 which are annular in shape as shown inFig. 6 . Thecavity plates 62 are received in recesses formed in the housing 12, one on each side of the centering plate 28, so that they form surfaces against which wear plates 64 slide. Thecavity plates 62 partially close off the open end of the lubrication reservoirs 66 that are formed in each half of the housing 12. By closing these openings of the reservoirs 66 off, thecavity plates 62 impede the escape of lubricant from the reservoirs 66. - In addition, since the
cavity plates 62 enlarge the area of the wear surfaces of thecavity 29 defined by the housing 12 in which the centering plate 28 and wear plates 64 are received and orbit, they reduce wear of the wear plates 64. In addition they make it less likely that the centering disc 28 or wear plates 64 will tip relative to the housing 12 in thecavity 29 in which the centering plate 28 and wear plates 64 orbit. Thecavity plate 62 should be made of a dimensionally stable material that presents a good wear surface, such as steel, nylon or a similar material. For example, one material found suitable is spring steel. Thecavity plates 62 are received in grooves, one formed in each housing half (the housing halves are bolted together to form the housing 12) and are kept in these grooves by the centering plate 28 and wear plates 64 holding thecavity plates 62 spaced apart. However, thecavity plates 62 could be bonded or otherwise secured to each housing half. -
Figs. 7 and8 illustrate a second embodiment 110 that is very similar to the first embodiment 10. In this embodiment, elements corresponding to elements of the first embodiment 10 are labeled with the same reference number plus 100. - The embodiment 110 differs from the embodiment 10 in that it has an
additional seal 172 between theball retainer 132 and theball cavity 118, to help retain lubricant in the ball cavity, and has an additional seal 174 on each face of the centeringplate 128, at each circumferential corner as illustrated inFig. 7 . Aseal 178 is also provided at the inner diameter of eachplate 162 and is bonded thereto to create a sliding seal with the adjacent plate 164 Theseals 174 and 178 help retain lubricant in thecenter cavity 29 area of thehousing 112. Theseals 172 and 174 could be provided as o-ring seals as illustrated, or could be provided as bonded-on lip seals like theseal 40. - A third embodiment 210 having additional seals is illustrated in
Fig. 9 . In this embodiment, elements corresponding to elements of the second embodiment 110 are labeled with the same reference number plus 100. - The embodiment 210 differs from the embodiment 110 by having an alternative for the seal 174, which is a band seal 276 provided around the outside circumference of the centering plate 28 as illustrated in
Fig. 9 . The edges of the seal 276 create a sliding seal with the plates 264 that helps retain lubricant in the center cavity 229 of thehousing 212.Seals 172 are not illustrated in this embodiment, but could be. -
Figs. 10 and 11 illustratealternative lubrication passageways 79 and 80 running radially through the centering plate 28 that communicate withaxial passageway 82 of embodiment 10. Only one is shown in each centering plate although more than one may be provided. Thepassageway 82 runs through the plate 28 and pins 26 to provide communication between theball sockets 18, and thepassageway 79 or 80 provides communication from thecenter cavity 29 of the housing to thepassageway 82, and therefore to theball sockets 18.Fig. 10 illustrates thepassageway 79 made using a center drill andFig. 11 illustrates the passageway 80 made using a standard drill bit and controlling the drill point break-through depth. Bothpassageways 79 and 80 have a smaller diameter hole at its inner end that acts as an orifice to regulate the flow of grease passing between the center cavity grease reservoir and the two ball sockets. This smaller diameter hole creates resistance to flow and therefore creates a pressure difference when filling with grease and when running. Thepassageways 79 or 80 can be applied to any of the embodiments of the invention. - Preferred embodiments of the invention have been described in considerable detail. Many modifications and variations to the preferred embodiments described will be apparent to persons skilled in the art. Therefore, the invention should not be limited to the preferred embodiments described, but should be defined by the claims which follow.
Claims (23)
- A universal joint (10) of the type having a pair of yokes (14) pivotally connected to one another with a centering apparatus (28) between the yokes (14) including at least one ball (20) received within a ball socket (18), wherein the ball (20) is retained in the ball socket (18) by a ball retainer (32)having: (a) a retainer body (36) that is rigid and retains the ball (20) axially in the socket (18); and (b) an elastomeric seal (40) bonded to an axial end surface of the retainer body (36) so as to wipe against a spherical surface (22) of the ball (20) as the ball (20) rotates relative to the ball retainer (32), characterized in that the retainer body (32) is axially secured to one of the yokes (14) and retains the ball (20) axially in the socket (18) relative to one of the yokes (14), and wherein the elastomeric seal (40) is axially fixed relative to one of the yokes (14).
- The universal joint of Claim 1, wherein the seal (40) is received in a recess in an end face of the retainer body (36).
- The universal joint of Claim 1, wherein a spherical surface (30) is formed on the retainer body (32) that mates with a spherical surface (22) of the ball (20), and a spherical surface is formed on the seal (40) that mates with the spherical surface (22) of the ball (20).
- The universal joint of Claim 1, wherein in a free state the seal (40) extends further radially inward than the retainer body (36).
- The universal joint of Claim 1, wherein the seal (40) has a U-shaped cross-section.
- The universal joint of Claim 1, wherein the seal (40) has an inner leg (46) that extends inward radially of the retainer body (36).
- The universal joint of Claim 1, wherein the seal (40) has an inner leg (46) that extends axially from the retainer body and radially inward from the retainer body (36).
- The universal joint of Claim 1, wherein in an extreme position of the universal joint (10) the seal (40) provides a soft stop that limits further angulation of the universal joint (10).
- The universal joint of Claim 1, wherein the seal (40) provides an edge (52) that wipes lubricant on the spherical surface (22) of the ball (20) rearwardly relative to the ball back into the ball socket (18) as the ball (20) rotates out of the seal (40).
- The universal joint of Claim 1, wherein when the retainer (32) is assembled to the ball (20), the ball (20) expands the diameter of the elastomeric seal (40).
- The universal joint of Claim 1, wherein the seal (40) has a rounded outer edge.
- The universal joint of Claim 1, further comprising a seal (172) between the retainer body and the ball socket.
- A double universal joint (10) having a pair of yokes pivotally connected to one another by a housing (12) and a centering apparatus between the yokes including a centering plate (28) received in a cavity (29) of the housing (12) wherein surfaces of the cavity are defined at least in part by axially extending recesses, wherein at least one cavity plate (62) is received in the cavity (66) held axially and radially fixed relative to the housing (12) such that the cavity plate (62) at least partially closes off at least one of said axially extending recesses (66).
- The double universal joint of Claim 13, wherein the cavity plate is annular.
- The double universal joint of Claim 13, wherein two cavity plates (62) are provided, and each cavity plate (62) partially closes at least one axially extending recess, one on each side of the centering plate (28).
- The double universal joint of Claim 13, wherein an axially inwardly facing surface of the cavity plate (62) provides an enlarged wear surface.
- The double universal joint of Claim 13, wherein at least one wear plate (64) is provided between the cavity plate (62) and the at least one centering plate (28), the wear plate (64) sliding against an axially facing surface of the centering plate (28) and sliding against an axially facing surface of the at least one cavity plate (62).
- The double universal joint of Claim 17, wherein at least one elastomeric seal is provided between the centering plate and the at least one wear plate.
- The double universal joint of Claim 17, wherein at least one elastomeric seal is provided between the at least one wear plate and the at least one cavity plate.
- The double universal joint of Claim 13, wherein the cavity plate is received in a recess of the cavity in which the centering plate orbits.
- The double universal joint of claim 13, wherein a pair of cavity plates (62) are provided in the recess (66), one on each side of the centering plate (28), and the cavity plates (62) are fixed axially and radially so as to partially close off an opening into an axially extending lubrication reservoir recess (66).
- A double universal joint according to any of the preceding claims, having a pair of yokes pivotally connected to one another by a housing and a centering apparatus between the yokes including a centering plate received in a cavity of the housing, each yoke having a ball socket that is connected to the centering plate, wherein the centering plate includes passageways that connect the ball sockets with the cavity of the housing through at least one orifice that restricts lubricant flow from the cavity to the ball sockets.
- The double universal joint of claim 13, wherein the passageways include at least one radially extending passageway that communiates at an inner end with the orifice.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/051,912 US7235016B2 (en) | 2005-02-04 | 2005-02-04 | Universal joint lubrication |
Publications (3)
Publication Number | Publication Date |
---|---|
EP1688632A2 EP1688632A2 (en) | 2006-08-09 |
EP1688632A3 EP1688632A3 (en) | 2007-03-28 |
EP1688632B1 true EP1688632B1 (en) | 2010-12-15 |
Family
ID=35911121
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP06001834A Not-in-force EP1688632B1 (en) | 2005-02-04 | 2006-01-30 | Universal joint lubrication improvements |
Country Status (5)
Country | Link |
---|---|
US (2) | US7235016B2 (en) |
EP (1) | EP1688632B1 (en) |
AT (1) | ATE491894T1 (en) |
CA (1) | CA2535250C (en) |
DE (1) | DE602006018810D1 (en) |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP5063280B2 (en) * | 2007-09-28 | 2012-10-31 | 株式会社日立製作所 | File transfer system, client, server |
IT201800009788A1 (en) * | 2018-10-25 | 2020-04-25 | Edi Bondioli | WIDE ANGLE CV JOINT WITH LUBRICANT TANK |
CN112363427B (en) * | 2020-10-28 | 2021-08-31 | 浙江树人学院(浙江树人大学) | Servo motor drive control system for industrial robot |
CN112196911B (en) * | 2020-11-09 | 2023-07-21 | 中国船舶重工集团公司第七0三研究所 | Lubricating device for high-speed gear type coupling |
CN112524167B (en) * | 2020-12-22 | 2021-10-15 | 泰尔重工股份有限公司 | Drum-shaped gear coupling with axial large-expansion function |
WO2022135801A1 (en) * | 2020-12-22 | 2022-06-30 | Comer Industries S.P.A. | Wide-angle constant-velocity joint with optimized lubrication |
CN114412915B (en) * | 2022-03-30 | 2022-06-07 | 达州市卡雷亚数控机床有限公司 | Transmission device with bearing and shaft |
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US1911214A (en) | 1928-08-22 | 1933-05-30 | Manning & Co | Universal joint |
US1987807A (en) | 1929-08-14 | 1935-01-15 | Mechanics Universal Joint Comp | Universal joint assembly |
US2991634A (en) | 1960-07-29 | 1961-07-11 | Gen Motors Corp | Universal joint centering device |
US3120746A (en) | 1962-01-22 | 1964-02-11 | Dana Corp | Pressure equalizing means for a double cardan joint centering device |
US3848938A (en) * | 1973-02-28 | 1974-11-19 | Torrington Co | Bearing and bearing seal |
US3947077A (en) * | 1973-04-18 | 1976-03-30 | Caterpillar Tractor Co. | Sealed ball and socket connection |
DE2802572C2 (en) * | 1978-01-21 | 1982-07-22 | Jean Walterscheid Gmbh, 5204 Lohmar | Homokinetic double joint for large flexion angles |
DE2833149C2 (en) | 1978-07-28 | 1980-08-28 | Gelenkwellenbau Gmbh, 4300 Essen | Double cardan joint |
FR2456875A1 (en) | 1979-05-15 | 1980-12-12 | Dba | BALL JOINT |
DE3138190C2 (en) * | 1981-09-25 | 1983-08-11 | Jean Walterscheid Gmbh, 5204 Lohmar | Greasable wide-angle joint |
DE3142930C2 (en) * | 1981-10-29 | 1983-08-25 | Jean Walterscheid Gmbh, 5204 Lohmar | Greasable wide-angle joint |
US4650439A (en) * | 1984-12-10 | 1987-03-17 | Weasler Engineering, Inc. | Centering apparatus for constant velocity universal joint |
US4781662A (en) * | 1985-11-14 | 1988-11-01 | Weasler Engineering, Inc. | Universal joint with improved lubrication |
DE8536143U1 (en) * | 1985-12-21 | 1986-02-20 | SKF Gleitlager GmbH, 6625 Püttlingen | Arrangement for sealing bearings, in particular spherical plain bearings with an outer ring composed of two half-shells |
DE3636194C1 (en) | 1986-10-24 | 1988-06-30 | Walterscheid Gmbh Jean | Homokinetic double joint |
DE8705293U1 (en) * | 1987-04-09 | 1987-07-09 | SKF Gleitlager GmbH, 6625 Püttlingen | Device for sealing bearings, in particular spherical bearings |
US4966488A (en) * | 1987-09-18 | 1990-10-30 | Weasler Engineering, Inc. | Ball retainer |
GB8925421D0 (en) * | 1989-11-10 | 1989-12-28 | Boc Group Plc | Shaft sealing arrangements |
GB9016481D0 (en) | 1990-07-27 | 1990-09-12 | Gkn Cardantec | Double hookes universal joints |
US5419740A (en) | 1992-03-16 | 1995-05-30 | Toyota Jidosha Kabushiki Kaisha | Constant velocity joint having centering disk bearing eccentric socket |
US5573336A (en) * | 1995-08-31 | 1996-11-12 | The Torrington Company | Seal for a spherical plain bearing |
US5688065A (en) | 1995-10-25 | 1997-11-18 | Weasler Engineering, Inc. | Double cardan universal joint ball and socket seal |
DE10005988B4 (en) * | 2000-02-09 | 2005-10-20 | Zf Lemfoerder Metallwaren Ag | ball joint |
DE10005979C5 (en) * | 2000-02-09 | 2010-07-22 | ZF Lemförder GmbH | ball joint |
DE10120432A1 (en) * | 2001-04-26 | 2002-11-14 | Walterscheid Gmbh Gkn | Centered double universal joint |
US6626575B2 (en) * | 2001-06-07 | 2003-09-30 | Roller Bearing Company Of America | Spherical plain bearing with spread lock dual sealing means |
DE10135347B4 (en) * | 2001-07-20 | 2012-06-14 | Gkn Walterscheid Gmbh | Centered double universal joint |
DE10135346A1 (en) * | 2001-07-20 | 2003-02-06 | Walterscheid Gmbh Gkn | Centered double universal joint |
-
2005
- 2005-02-04 US US11/051,912 patent/US7235016B2/en active Active
-
2006
- 2006-01-30 DE DE602006018810T patent/DE602006018810D1/en active Active
- 2006-01-30 AT AT06001834T patent/ATE491894T1/en not_active IP Right Cessation
- 2006-01-30 EP EP06001834A patent/EP1688632B1/en not_active Not-in-force
- 2006-02-03 CA CA2535250A patent/CA2535250C/en not_active Expired - Fee Related
-
2007
- 2007-05-09 US US11/746,419 patent/US20070207864A1/en not_active Abandoned
Also Published As
Publication number | Publication date |
---|---|
US20070207864A1 (en) | 2007-09-06 |
US20060177261A1 (en) | 2006-08-10 |
CA2535250A1 (en) | 2006-08-04 |
CA2535250C (en) | 2013-07-30 |
EP1688632A3 (en) | 2007-03-28 |
DE602006018810D1 (en) | 2011-01-27 |
EP1688632A2 (en) | 2006-08-09 |
US7235016B2 (en) | 2007-06-26 |
ATE491894T1 (en) | 2011-01-15 |
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